JP3161244B2 - Transmission synchronization device - Google Patents

Description

DETAILED DESCRIPTION OF THE INVENTION

[0001]

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a transmission for a vehicle, and more particularly to a synchronizing device used in a manual transmission.

[0002]

2. Description of the Related Art The basic structure of a synchronizer used in a manual transmission for a vehicle will be described with reference to FIG.
No. 15221 is a single cone type synchronizing device, in which a clutch hub 2 is spline-fitted to a rotating shaft 1, and synchronized gears 3, 4 are rotatable on both left and right sides of the clutch hub 2. Are located. On the clutch hub 2 side of these synchronized gears 3 and 4,
Spline pieces 5 and 6 are spline-fitted.
Further, a tapered cone portion 7 is provided on the outer peripheral portion of the boss portion extending toward the clutch hub 2 among the spline pieces 5 and 6.
Synchronizer rings 9 and 10 are formed in these tapered cone portions 7 and 8 in a predetermined size in the axial direction.
It is movably fitted. A hub sleeve 11 is engaged with the outer peripheral portion of the clutch hub 2 so as to be movable only in the axial direction, and chamfers are formed at both inner peripheral end portions of the hub sleeve 11. , 10 are formed with chamfers, and splines that engage with the hub sleeve 11 are formed on the outer peripheral portions of the spline pieces 5, 6.

In the above-described synchronizing device, when the hub sleeve 11 is moved to one of the synchronized gears 3 and 4, the synchronizer rings 9 and 10 are pushed by a key (not shown) and the spline piece is moved. Move to 5,6 side. As a result, the synchronizer rings 9 and 10 are engaged with the spline pieces 5 and 6 by the tapered cone portions 7 and 8 and start to rotate synchronously. When the hub sleeve 11 is further moved after the chamfer of the hub sleeve 11 and the chamfer of the synchronizer rings 9 and 10 are in contact with each other, the hub sleeve 11 pushes the chamfers of the synchronizer rings 9 and 10 forward and advances. With the spline.

[0004] Synchronizer rings 9 and 10 in the synchronizing device act when the hub sleeve 11 is engaged with the spline pieces 5 and 6 on the side of the gears 3 and 4 to be synchronized. The synchronizer rings 9 and 10 are rotating together with the clutch hub 2 in a state where a predetermined gear is set by a non-rotating gear. However, when no force is applied to move the synchronizer rings 9 and 10 toward the clutch hub 2, the synchronizer rings 9 and 10 may engage with the spline pieces 5 and 6 via the tapered cone portions 7 and 8. Since the synchronizer rings 9 and 10 rotate with the clutch hub 2 while the spline pieces 5 and 6 rotate with the synchronized gears 3 and 4 at a different speed, the taper cone portions 7 and 10 rotate. In FIG. 8, slippage occurs, where sliding friction occurs. Such friction generates drag torque, which causes a power loss, a rise in lubricating oil temperature, and a shortening of the life of the synchronizer ring. In addition, the synchronizer ring is distorted due to stick slip at the time of contact (so-called rattling). (Sounding noise).

Therefore, in the conventional synchronizing device shown in FIG. 7, the radius of the clutch hub 2 gradually increases from both ends in the axial direction toward the center on the back surface, that is, the inner peripheral surface of the portion where the hub sleeve 11 is engaged. Tapered surfaces 12 and 13 where
On the other hand, holes 14 and 15 are formed in the synchronizer rings 9 and 10 along the radial direction, and these holes 14 and 15 are formed.
A ball 16 and an inertia mass body 17 are movably accommodated in the ball 15, and the balls 16 and 17 are configured to protrude to the outer peripheral side by centrifugal force.

Therefore, the synchronizer rings 9 and 10 on the spline pieces 5 and 6 side with which the hub sleeve 11 is not engaged are pushed to the outer peripheral side by the centrifugal force, so that the balls 16 and 17 are disengaged from the clutch. Since it is going to move toward the center in the axial direction along the tapered surfaces 12 and 13 of the hub 2, it is urged in a direction away from the spline pieces 5 and 6 and the tapered cone portions 7 and
8 slippage is eliminated.

[0007]

In the above-mentioned conventional synchronizer, the centrifugal force acting on the balls 16 and 17 is reduced by the tapered surface 1.
The synchronizer rings 9 and 10 are converted into axial forces by the axial forces 2 and 13, and the synchronizer rings 9 and 10 are returned by the axial force. Since these are small components that move in the direction, the balls 16 and 17 that can be held by the components must be small and small in mass. In addition, it is difficult to make the taper angles of the tapered surfaces 12 and 13 that can be formed on the clutch hub 2 large in order to secure the strength of the clutch hub 2. The resulting axial force must be small.

Therefore, in the above-mentioned conventional synchronizing device, it is difficult to generate an axial force sufficient to return the synchronizer rings 9 and 10 to the return position. In particular, in order to prevent rattling noise, the synchronizer ring is connected to the spline piece. In a synchronizer provided with an elastic body that presses to the side, an axial force that overcomes the elastic force of the elastic body is required. Therefore, it is practically not practical to adopt the above-described conventional mechanism in this type of synchronizer. It was impossible.

SUMMARY OF THE INVENTION The present invention has been made in view of the above circumstances, and is directed to a transmission in which it is easy to sufficiently increase a return movement force for eliminating a drag torque between a synchronizer ring and a synchronized rotating body. It is an object to provide a synchronization device.

[0010]

According to the present invention, in order to achieve the above object, the inertial mass acting on the centrifugal force is held by a clutch hub to increase the size of the inertial mass, and the centrifugal force is increased. An inclined surface for generating an axial force is formed on a projection provided on the synchronizer ring to increase the angle.

More specifically, according to the present invention, the hub sleeve is movably engaged with the outer peripheral portion of the clutch hub attached to the rotating body only in the axial direction, and the hub sleeve is moved in the axial direction. A synchronized rotating body that is engaged with the hub sleeve is disposed adjacent to the clutch hub and rotatably with respect to the rotating body, and approaches the synchronized rotating body or a member that rotates integrally with the synchronized rotating body. A synchronizer for a transmission in which a synchronizer ring that transmits torque between the synchronized rotating body or a member that rotates integrally with the synchronized rotating body is disposed, and the outer peripheral portion is radially outwardly moved by centrifugal force. The inertial mass body that moves to is held by the clutch hub, and a protruding portion extending to the outer peripheral side of the inertial mass body is provided integrally with the synchronizer ring, An inclination that generates an axial force that presses the synchronizer ring in a direction away from the synchronized rotary member based on the centrifugal force of the inertial mass at a portion of the protrusion that is radially opposed to the inertial mass. The surface is formed.

In the present invention, an elastic member for pressing the synchronizer ring toward the synchronized rotating body can be provided.

[0013]

In the present invention, the synchronizer ring moves toward the synchronized rotating body to make frictional contact with the synchronized rotating body, and as a result, torque is transmitted between the two. On the other hand, when the clutch hub rotates, a centrifugal force acts on the inertial mass body held by the clutch hub, and tends to move outward in the radial direction. As a result, the inertial mass comes into contact with the inclined surface formed on the protrusion of the synchronizer ring, where an axial force based on centrifugal force is generated, and a load acts in a direction separating the synchronizer ring from the synchronized rotating body. . The acting force in the axial direction is determined by the centrifugal force acting on the inertial mass and the angle of the inclined surface, but since the inertial mass is held by a clutch hub having a dimensional margin, it is necessary to be large enough. The angle can be made sufficiently large because the inclined surface is formed in a projection integrated with the synchronizer ring. As a result, the obtained acting force in the axial direction is increased, the synchronizer ring is separated from the synchronized rotating body, and the friction between the two and the drag torque resulting therefrom can be eliminated.

If an elastic member is provided for pressing the synchronizer ring toward the synchronized rotating body, the synchronizer ring contacts the synchronized rotating body in a state where the centrifugal force is small, and torque transmission is generated between the two. As a result, an urging force for rotating the synchronized rotating body in a predetermined direction is generated, and so-called rattling does not occur even when the rotation angular velocity fluctuates greatly. On the other hand, if the centrifugal force is large, a load is generated in the direction of separating the synchronizer ring from the synchronized rotating body as described above, and since the acting force in the axial direction is sufficiently large, it resists the elastic force of the elastic member. Thus, the synchronizer ring can be separated from the synchronized rotating body. As a result, the drag torque between the synchronizer ring and the synchronized rotating body can be eliminated.

[0015]

Next, the present invention will be described in detail based on embodiments. 1 to 3 are sectional views showing an embodiment of the present invention, in which a clutch hub 21 is spline-fitted to a shaft 20 which is stationary in a neutral state, that is, a state in which the transmission does not transmit torque. Keys 22 are attached at a plurality of positions (three positions in the illustrated example) on the outer peripheral side so as to be slidable in the axial direction.
2 is pressed to the outer periphery by a spring 23 arranged on the inner periphery. In addition, concave portions 24 are formed radially at a plurality of positions (three positions in the illustrated example) on the outer peripheral side of the clutch hub 21, and a ball 25 as an inertial mass body protrudes radially in these concave portions 24. It is retractably stored. Further, a hub sleeve 26 is spline-fitted to the outer peripheral side of the clutch hub 21 and is mounted so as to be movable only in the axial direction.

Gears 27 and 28 having different diameters are arranged on both sides of the clutch hub 21, and these gears 27 and 28 are rotatably fitted to the shaft 20 via bearings 29 and 30. ing. These gears 27, 2
8 meshes with a gear formed on the input shaft 31.

Each of the gears 27 and 28 has a clutch hub 21.
Bosses protruding to the sides are formed, and spline pieces 32 and 33 are spline-fitted to the respective bosses. Each of the spline pieces 32 and 33 has a spline that meshes with the hub sleeve 26 on the outer peripheral portion, and each of the boss portions has a tapered portion having a small diameter on the clutch hub 21 side. Synchronizer rings 34 and 35 are loosely fitted to the outer peripheral side of.

These synchronizer rings 34, 35
Are formed as tapered surfaces corresponding to the tapered portions of the spline pieces 32, 33, and the tapered surfaces 32a, 33a of the spline pieces 32, 33 and the tapered surfaces 34a of the synchronizer rings 34, 35 corresponding thereto. ,
35a comes into contact with the spline piece 3
The torque transmission is generated between the synchronizers 2 and 33 and the synchronizer rings 34 and 35. That is, the tapered cone portion is formed here.

An elastic member 36 for pressing the synchronizer ring 34 toward the spline piece 32 is interposed between the synchronizer ring 34 on the right side in FIG. As the elastic member 36, an appropriate one such as a coil spring or a disc spring can be used.
In the illustrated example, the wave spring shown in FIG. 4 is used. Therefore, the synchronizer ring 34 is pressed by the elastic force toward the spline piece 32, and is in sliding contact with the tapered cone portion between the two so as to transmit torque.

Further, in the synchronizer ring 34, at a position corresponding to the ball 25 as the inertial mass body, a plate-like projection 37 extending to the outer peripheral side of each ball 25 is provided.
Are formed integrally, and the tip portion of each projection 37 is
The outer peripheral surface of each ball 25 is bent inward so as to embrace a portion on the side opposite to the wave spring 36 side, and an inclined surface 38 whose angle with respect to the radial direction is formed here. That is, the inclined surface 38 is
The synchronizer ring 34 is moved to the left in FIG. 1, that is, the wave spring 36 is compressed and the spline piece 32 is
The acting force is generated in a direction away from the object.

In the synchronizing device described above, when the hub sleeve 26 is in the neutral state as shown in FIG. 1, the shaft 20 and the clutch hub 21 are stopped without rotating, whereas the input shaft 3 is stopped.
As a result, the gears 27 and 28 rotate. In this state, the synchronizer ring 3 on the right side of FIG.
4 is pressed to the spline piece 32 side by the wave spring 36, and both are contacted by the taper cone portion,
Here, a friction torque is generated. That is, the torque in the rotating direction of the gear 27 acts on the synchronizer ring 34, the hub sleeve 26, and the clutch hub 21, and as a result, rattling in the rotating direction is blocked, so-called rattling noise (toothing noise) is prevented. You.

On the other hand, when the clutch hub 21 rotates together with the shaft 20 during traveling, a centrifugal force acts on the ball 25. The centrifugal force increases as the number of rotations increases, and the ball 25 tends to protrude outward in the radial direction from the recess 24. Then, the ball 25 is synchronizer ring 34
Comes into contact with the inclined surface 38 formed on the projection portion 37 of the boss, and accordingly, an axial force in a direction of separating the synchronizer ring 34 from the spline piece 32 is applied.

The magnitude of the axial force is substantially determined by the inclination angle θ of the inclined surface 38. In the configuration shown in FIGS.
4, the inclined surface 38
Is not particularly limited, that is, since the inclination angle θ of the inclined surface 38 is set to be considerably large, the axial force acting on the synchronizer ring 34 becomes a large load. As a result, at a predetermined rotational speed or more, the synchronizer ring 34 can be completely separated from the spline piece 32 against the elastic force of the wave spring 36,
Therefore, sliding contact between the spline piece 32 and the synchronizer ring 34 can be eliminated, and so-called drag torque can be prevented from being generated at this portion.

FIG. 5 shows the relationship between the rotational speed of the shaft and the drag torque. When the rotational speed of the shaft exceeds a predetermined rotational speed, the axial force Fb caused by the centrifugal force is reduced. Since it is larger than the resistance force Fa due to the elastic force or the frictional force due to the wave spring 36, the contact between the spline piece 32 and the synchronizer ring 34 at the tapered cone portion is eliminated, and the drag torque becomes zero.

The synchronizing operation of the synchronizing device shown in FIG. 1 is substantially the same as that of the conventional one. When the hub sleeve 26 is moved in the axial direction, the key 22 moves together with the hub sleeve 26 in the axial direction. , The synchronizer rings 34 and 35 are pressed in the axial direction, so that
The tapered surfaces 34a, 35a on the inner peripheral side come into contact with the corresponding tapered surfaces 32a, 33a of the spline pieces 32, 33, and both start rotating synchronously. And hub sleeve 26
And the chamfers of the synchronizer rings 34 and 35 come into contact with each other, and the hub sleeve 36 further moves in the axial direction, so that the synchronizer ring 3
The hub sleeve 26 is moved toward the spline pieces 32 and 33 by pushing and separating the chamfers 4 and 35, and finally engages with the splines to complete the shift.

FIG. 6 shows another embodiment of the present invention. In the synchronizer shown here, a clutch hub 21 is mounted on a gear 40 which is stationary at the time of idling, and a counter for idling a spline piece 32 therewith. This is an example of attachment to a shaft 41. That is, the gear 40 is rotatably mounted on the countershaft 41 via the bearing 42, and the clutch hub 21 is spline-fitted to the outer peripheral side of the boss portion. Other configurations are almost the same as those of the embodiment shown in FIG. 1, and therefore, the same reference numerals as in FIG. 1 are assigned to FIG. 6 and the description thereof is omitted.

In the configuration shown in FIG. 6, the counter shaft 41 rotates at the time of idling, whereas the gear 40 and the clutch hub 21 are stationary without rotating, but the synchronizer ring 34 is splined by the wave spring 36. 32 side, and as a result,
Sliding contact is made at the tapered cone portion between the two, where torque is transmitted. Since a load in the rotational direction acts on the synchronizer ring 34 and the clutch hub,
Even in a so-called neutral state, generation of rattling noise (rattling noise) is prevented.

On the other hand, if the clutch hub 21 rotates together with the gear 40 during traveling, a centrifugal force acts on the ball 25, and as a result, the projection 37 is attached to the synchronizer ring 34.
An axial force directed to the left in FIG. 6 acts via the inclined surface 38 at the point, so that the synchronizer ring 34 is separated from the spline piece 32, and the sliding contact between the two is eliminated. That is, drag torque between the synchronizer ring 34 and the spline piece 32 is prevented.

As described above, in each of the above-described embodiments, the ball 25 which moves outward in the radial direction due to the centrifugal force is held by the clutch hub 21 having a sufficient dimension.
The ball 25 can be much larger than the conventional device shown in FIG. Also, an inclined surface 3 for converting a load directed outward in the radial direction into an acting force directed in the axial direction.
Since 8 is formed on the projection 37 of the synchronizer ring 34, the angle of the inclined surface 38 can be made large without any particular restriction. Therefore, in addition to the large centrifugal force by the ball 25, the large axial angle force can be obtained by the large inclination angle θ of the inclined surface 38. As a result, in a state where the clutch hub 21 is rotating, the synchronizer ring 34 can be reliably separated from the spline piece 32 to eliminate the drag torque therebetween, thereby preventing power loss and improving fuel efficiency. Can be planned.

Further, since the axial force is large, the synchronizer ring 34 is pressed toward the spline piece 32 by an elastic body such as the wave spring 36 used in each of the above-described embodiments to eliminate rattling during neutral or idling. Even in the case where the synchronizer ring 34 is constructed, the synchronizer ring 34 can be separated from the spline piece 32 against the elastic force of the elastic body 36 at the time of traveling, and as a result, the rattling sound at the time of neutral or idling ( Drag torque can be prevented in addition to prevention of rattling noise).

In the above-described embodiment, an example is shown in which a ball is used as the inertial mass body. However, the present invention is not limited to each of the above-described embodiments, and the shape of the inertial mass body may be arbitrary. For example, it may be a pin having a spherical end surface or a shaft. With such a shape,
It is possible to further increase the mass of the inertial mass.

In each of the above embodiments, a single cone type synchronizing device has been described as an example. However, the present invention can also be applied to a double cone type synchronizing device or a triple cone type synchronizing device. it can.
When the present invention is applied to these multi-cone type synchronizers, since the power loss due to the drag torque at the outer peripheral side tapered cone portion is large, the axial force based on the centrifugal force acting on the inertial mass body is reduced at the outer peripheral side. It is preferable to configure so as to act on the synchronizer ring.

[0033]

As described above, according to the synchronizing apparatus of the present invention, the inertial mass on which the centrifugal force acts is held by the clutch hub. A large centrifugal force can be obtained by increasing the size of the body. In addition, since the inclined surface that converts the load based on the centrifugal force of the inertial mass body into the axial force is formed on the protrusion integrated with the synchronizer ring, it is possible to increase the inclination angle of the inclined surface without being particularly limited. As a result, the axial force with respect to the radially outward load caused by the centrifugal force can be increased.

Therefore, according to the present invention, the centrifugal force itself can be increased, and this can be converted into a large axial force, so that the synchronizer ring can be reliably removed from the synchronized rotating body such as a spline piece. By separating them, the drag torque between them can be eliminated. In particular, even when an elastic member that presses the synchronizer ring toward the synchronized rotating body is used to prevent rattling noise (rattling sound), the elastic force is large due to the large axial force. This allows the synchronizer ring to be separated from the rotating body to be synchronized, thus preventing rattling noise (rattling noise) at low rotation speeds and effectively eliminating drag torque at high rotation speeds. Become.

[Brief description of the drawings]

FIG. 1 is a sectional view showing an embodiment of the present invention.

FIG. 2 is a sectional view taken along line II-II of FIG.

FIG. 3 is a partial sectional view of a part III in FIG. 1;

FIG. 4 is a side view of a wave spring.

FIG. 5 is a diagram showing a relationship between a rotation speed of a shaft and a drag torque.

FIG. 6 is a sectional view showing another embodiment of the present invention.

FIG. 7 is a cross-sectional view illustrating an example of a conventional synchronization device.

[Explanation of symbols]

 Reference Signs List 21 clutch hub 25 ball 26 hub sleeve 32, 33 spline piece 34, 35 synchronizer ring 36 elastic member (wave spring) 37 protrusion 38 inclined surface

──────────────────────────────────────────────────続 き Continuation of the front page (56) References JP-A-8-49732 (JP, A) JP-A-3-115221 (JP, U) JP-A 62-108652 (JP, U) JP-A-2- 21338 (JP, U) (58) Field surveyed (Int. Cl. ⁷ , DB name) F16D 23/04-23/06

Claims (2)

(57) [Claims] 1. A synchronized sleeve in which a hub sleeve is movably engaged only in an axial direction with an outer peripheral portion of a clutch hub attached to a rotating body, and is engaged with the hub sleeve by moving the hub sleeve in an axial direction. A rotating body is disposed adjacent to the clutch hub and rotatably with respect to the rotating body, and the synchronized rotating body approaches the synchronized rotating body or a member that rotates integrally with the synchronized rotating body. Alternatively, in a transmission synchronizing apparatus in which a synchronizer ring for transmitting torque between the synchronized rotating body and a member that rotates integrally is disposed, the inertial mass body that moves outward in a radial direction by centrifugal force is the clutch hub. And a projection extending to the outer peripheral side of the inertial mass body is provided integrally with the synchronizer ring. An inclined surface that generates an axial force that presses the synchronizer ring in a direction away from the synchronized rotating body based on the centrifugal force of the inertial mass body is formed at a position radially opposed to the body. A synchronizing device for a transmission. 2. The transmission synchronizing device according to claim 1, further comprising an elastic member that presses the synchronizer ring toward the synchronized rotating body.